Shaft structure in screw rotor of screw fluid assembly

ABSTRACT

A rotor  1  forming screw teeth is projectingly provided at its outer end  2  on the axis thereof with a center shaft  3 . The center shaft  3  is provided at its outer end  4  with a smaller-diameter shaft  5  or a concaved fitting hole. A separate rotor shaft  6  which is to be fitted over the smaller-diameter shaft  5  or fitted into the concaved fitting hole is provided with another concaved fitting hole  7  or smaller-diameter shaft. A metal shaft around which synthetic resin is molded is formed at its peripheral surface with a spiral groove or corrugated groove in the opposite revolutional direction with respect to the revolutional direction of the screw rotor. The spiral groove is formed with smooth arc curved line connecting profiles of adjacent grooves. The shaft is provided with a step, and synthetic resin is molded around the shaft surface to form a screw rotor.

CROSS-REFERENCE

This patent application is a divisional application of patentapplication No. 09/111,446, filed on Jul. 8, 1998.

BACKGROUND OF THE INVENTION

1. Field of the Invention

The present invention relates to a shaft structure in a screw rotor usedin a screw fluid assembly, and more particularly to a joint structure ofa shaft of the screw rotor and a mounting structure of the shaft of thescrew rotor to the rotor for the screw rotor used in a compressor, anexpander, a vacuum pump and the like.

Conventionally, in a screw rotor of this kind, the rotor and the rotorshaft are integrally formed. For example, the rotor and the shaftcomprising the center shaft and the rotor shaft are worked out bymilling from the same metal material. Alternatively, it is proposed tomold a rotor made of synthetic resin material, for example, injectionmolding around the shaft made of metal to improve a processingefficiency and to reduce a gross weight.

2. Description of the Prior Art

Even if a size of the rotor is common to different kinds of machines,since a discharging pressure of the screw fluid assembly or a primedriving means are changed, or length, diameter of the shaft or surfacetreatment of the shaft is changed in accordance with usage of the screwfluid assembly, the manufacturing process of the rotor is complicated,and a large number of kinds of processes is required.

For such reasons, there are various problems. If the case of diameter ofvarious portions of the screw rotor is taken as an example, in general,a diameter of tooth portion of the rotor is three or four times greaterthan a diameter of the shaft. Therefore, there are following problemsconcerning manufacture:

(1) When the rotor and the shaft are worked out by lathing from the samemetal material, it is necessary to use a material having the sizecorresponding to the diameter of the rotor tooth portion, and to lathethe material to a desired shaft diameter by lathing operation.Therefore, this wastes materials and necessitates a number of steps forthe process.

(2) When a rotor made of thermosetting synthetic resin is integrallymolded around the shaft made of metal, this case only requires a metalmaterial having a diameter of the shaft. However, since the axial lengthof such metal material is too long with respective to its diameter, itis necessary to prepare a remedy for a prevention of oscillation ofcenter of a work at the time of working, which lowers the productivity.

(3) Further, the axial length of the rotor is also long, a mold of therotor is increased in size and price, and the workability at the time ofmolding is also inferior. Further, the operating performance for asurface treatment is likewise inferior.

(4) For example, when the rotor and the shaft are used for awater-injection type compressor or the like in which water is injectedinto a compressed space for cooling in the space and tightly sealing upthe space, and in which the shaft contacts with atmosphere or fluidincluding moisture, rust is generated when they are used for a longtime, which may cause a leakage of the shaft sealing portion or abnormalabrasion of the sliding portion.

(5) Even if the tooth size of the rotor is common, since the diameter orlength of the shaft is different, parts can not be used in common andthe manufacture and management are complicated.

As countermeasures or remedies for the above problems, Japanese UtilityModel Application Laid-open (Kokai) No.S57-105418 proposed to separatelywork out a hollow small-diameter portion and a hollow large-diameterportion of the screw rotor so as to reduce the weight, and to jointcorresponding opposed ends of both the portions by friction welding,thereby providing a screw compressor. This proposal is to hollow theshafts, and joint them by friction welding, and is not to solve theabove described various problems. Japanese Utility Model ApplicationLaid-open No.S56-49311 proposed to simply spline-connect crankshafts,and to charge elastic material to the spline-connected portions, therebyreducing both the friction and noise. Further, Japanese Utility ModelApplication Laid-open No.H2-71108 proposed to form a groove in one of apropeller shaft or a yoke, and to form, on the other, a projection to bemeshed with the groove. Furthermore, Japanese Patent Publication(Kokoku) No.S52-25562 proposed to integrally provide an impeller of acompressor with a sleeve having a threaded hole, and a threaded portionof a shaft is received in the threaded hole and assembled. However,these proposals are only related to a general mounting operation forenhancing the reliability, and are not for solving the above describedvarious problems.

A conventionally known screw rotor of this type is shown in FIG. 12 asan example relating to a screw rotor formed by molding a rotor made ofsynthetic resin by injection molding around the above described shaftmade of metal.

Each of FIGS. 12 (A) and 12 (B) show a female rotor, wherein FIG. 12 (A)is a partial sectional view taken along the line A—A in FIG. 12 (B), andFIG. 12 (B) is a front view thereof. A shaft 41 comprises a center shaft38 and a rotor shaft 36 of these screw rotors. The shaft 41 is formed atits peripheral surface with a single or a plurality of grooves 39 orprojections each having a square cross section (a quadrilateral) with alead angle in the torsion direction and its opposite direction of teeth46 of a rotor 1 f, thereby reinforcing a connecting force between theshaft 41 and the rotor 1 f to prevent them from leaving off (see, e.g.,Japanese Patent Applications Laid-open No.H6-123292 and No.1-301976).

In these screw rotors, rotor surfaces are formed of synthetic resin, andtherefore rust is not generated.

Therefore, the screw rotor of this kind is most suitable for a screwcompressor (water-injection type screw compressor) in which water isinjected in a space where compression action is performed (hereinafteralso called as a compression space).

In a screw rotor in which the groove 39 having a square cross section isformed on the peripheral surface of the shaft 41 and synthetic resinmaterial is molded thereon to connect the shaft 41 and the rotor 1 f,stress concentration is generated on an angle portion of the groove ofthe rotor (synthetic resin portion) corresponding to a crest of thegroove 39 provided on the shaft surface by a difference in a coefficientof linear thermal expansion based on difference in material of the shaftand the rotor at the time of cooling the rotor made of synthetic rotorafter injection molding, and by a difference in thermal shrinkagebetween the shaft 41 made of metal and the rotor made of synthetic resin(thermal shrinking amount of the shaft is small, and thermal shrinkingamount of the rotor is large) due to thermal change, at the further timeof driving the compressor and at the time of stopping the compressor,and by a large variation in revolutional torque due to variation in loadduring the driving.

By the above described reasons, in the screw rotor of this type, a crack51 is prone to be generated from the angle portion of the crest of thegroove 39 provided on the shaft surface toward the bottom of the toothof the rotor 1 f, and while driving and stopping operations of the screwrotor are repeated for a long time of period, there is a problem thatthe crack is spread and fixing force between the shaft 41 and the rotor1 f is lowered and finally the shaft and the rotor are separated.

On the other hand, when the case of the water-injection type screwcompressor is taken with reference to FIG. 6, if the screw rotor of theabove-described type is employed, since the rotor is made of syntheticresin, there is a characteristic that rust can be prevented. However,there is a problem that rust may be generated on the shaft surfacebecause the shaft 1 is made of metal, and the shaft surface between thecompression chamber and the shaft sealing portion (Water-shaft sealingdevice) contacts with water supplied in the compression chamber.

As described above, in the conventional screw rotor of thewater-injection type screw compressor, if rust is generated on the shaftportion, especially on the shaft surface into which a shaft sealingdevice for water is fitted, the shaft surface is corroded by the rust,and a diameter of such portion is reduced to cause a clearance betweenthe shaft sealing device, and the shaft surface or the shaft sealingdevice itself is damaged to lower the shaft-sealing performance.

As a result, water supplied to the compression chamber leaks from theclearance between the shaft sealing device and the shaft surface towardthe end of the shaft of the screw rotor, and flows into a bearingportion adjacent to the shaft sealing portion, which induces adeterioration of lubricant oil or emulsification to shorten life span ofthe bearing, and remedy therefor has been required.

Further, there are various problems that since the performance of theshaft sealing portion is lowered due to the generated rust, thelubricant oil supplied to the bearing portion flows into the compressionchamber from the clearance between the shaft sealing portion and theshaft surface and is mixed into the cooling and sealing water tocontaminate the water, and oil is also mixed in the discharged air,which exerts a harmful influence on apparatuses which consume thedischarged air.

Therefore, rust prevention remedies have been applied by using stainlesssteel as material for the screw rotor shaft, or plating or coating amaterial having high rust prevention effect on the shaft surface towhich the shaft sealing device is fitted. However, such remediesincrease the prices and working costs of the screw rotors.

SUMMARY OF THE INVENTION

The first and second objects of the present invention are to make itpossible by means of using a simple shaft connecting structure to employthe same rotors for various kinds of machines having different shaftlengths, to eliminate the waste of the screw rotor materials and toreduce the number of manufacturing steps to reduce the costs, andfurther to make it possible to separate the shafts to facilitate thehandling, to reduce the molding machine in size, and to lower themanufacturing costs by working out only an exclusive shaft among theshafts of various kinds of machine facilitating the working process ofthe shaft.

In addition to any of the first and second objects, the third object isto prevent an assembling error between the rotor and the rotor shaft, tofurther reduce the manufacturing costs.

In addition to any of the first to third objects, the fourth and fifthobjects are to make it possible to easily subject only a necessaryportion to a rust prevention treatment or surface treatment as a remedyof rust prevention of the shaft and employ the anticorrosive materialbecause synthetic resin is molded around the center shaft.

In addition to any of the first to fifth objects, the sixth object isthat an air passage hole passing from a fitting hole concaved in therotor shaft or the center shaft through a shaft end at opposite side isformed for smooth shaft connection so that the fitting operation of theshafts can easily and reliably be carried out, and air can flow(respiration) in the recess according to a difference in temperatureduring the operation and during the stoppage.

In addition to any of the first to sixth objects, the seventh and eighthobjects are that since the linear expansion coefficient of a material tobe fitted over the center shaft is smaller than that of a material ofthe center shaft, thereby generating an action in a direction to fastenthe fitting condition by conduction heat due to compressing action toreliably hold the fitted state for a long time of period.

The ninth object of the present invention is to solve all of theproblems indicated above concerning a screw rotor having a rotor made ofsynthetic resin around a shaft made of metal, to strengthen the fixingforce between the shaft and the rotor, to eliminate the stressconcentration around the fixing portion generated due to thermal change,to prevent the rust from being generated on the shaft surface in theshaft sealing portion, and to provide a low priced screw rotor having ahigh processing efficiency.

To achieve the first to eighth objects, according to the presentinvention, there is provided a shaft structure of a screw rotor for ascrew fluid assembly, comprising a rotor forming a screw teeth form anda center shaft projecting from at least one of outer ends of the rotoron an axis thereof, wherein the center shaft is provided at its outerend with a small-diameter shaft such as to form a step between the outerend of the center shaft and the small-diameter shaft, and a separaterotor shaft provided with a concaved fitting hole is fitted over thesmall-diameter shaft, thereby jointing both the shafts.

Alternatively, the shaft structure of a screw rotor for a screw fluidassembly, comprises a rotor forming a screw teeth form and a centershaft projecting from at least one of the outer ends of the rotor on anaxis thereof, wherein the center shaft is formed at its outer end with aconcaved fitting hole, and a separate rotor shaft from which asmall-diameter shaft is projected is fitted into the concaved fittinghole, thereby jointing both the shafts.

Further, to achieve the ninth object, according to the presentinvention, there a shaft made of metal around which synthetic resin ismolded is provided with a step and/or expanded portion, and the portionof the shaft around which synthetic resin is molded is provided at itssurface with a corrugated groove or spiral groove, and a cross sectionof the spiral groove or corrugated groove taken along the planeincluding the center line of the shaft is formed by an outlineconnecting adjacent arc groove surfaces so as to form a smooth arccurved line.

BRIEF DESCRIPTION OF THE DRAWINGS

The objects and advantages of the invention will become understood fromthe following detailed description of preferred embodiments thereof inconnection with the accompanying drawings in which like numeralsdesignate like elements, and in which:

FIG. 1 is a sectional view showing a screw rotor of the first embodimentof the present invention;

FIG. 2 is a sectional view showing the screw rotor before shafts arejointed according to the first embodiment of the present invention;

FIG. 3 is a sectional view of a screw rotor according to the secondembodiment of the present invention;

FIG. 4 is a sectional view of a screw rotor according to the thirdembodiment of the present invention;

FIG. 5 is a sectional view of a screw rotor according to the fourthembodiment of the present invention;

FIG. 6 is a schematic sectional view of an essential portion of anexample of a compressor or a conventionally known water-injection typescrew compressor;

FIGS. 7a-7 d are a side sectional view of a screw rotor and enlargedpartial sectional views of a spiral groove of one embodiment of thepresent invention;

FIG. 8 is a side sectional view of a screw rotor of another embodimentof the present invention;

FIG. 9 is a partial side sectional view of a screw rotor of anotherembodiment of the present invention;

FIG. 10 is a partial side sectional view of a screw rotor of anotherembodiment of the present invention;

FIG. 11 is a partial side sectional view of a screw rotor of anotherembodiment of the present invention: and

FIGS. 12a-12 b are a partial sectional view and a front view of oneexample of a conventionally known screw rotor.

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS

Although embodiments of a screw rotor of the present invention will bedescribed hereinafter with reference to the drawings, among subjectmatters constituting the embodiments, there are included ones which canvariously be modified by a person skilled in the art within a normaltechnical level in the art at the time when the present application wasfiled. Therefore, it is not allowed to interpret the subject matters ofthe present invention by defining based on a specific structuredisclosed in the embodiments without showing specific reasons.

The present invention will be described below, conveniently taking thecase of a screw fluid assembly as an example. The description will bemade based on the embodiments shown in FIGS. 1 to 5. As shown in FIGS. 1and 2, for example, a center shaft 3 is provided on a rotor 1 forming ascrew teeth, and the center shaft 3 is provided such as to extend fromat least one outer end 2 on the axis of the rotor 1, or by molding arotor made of synthetic resin around a shaft made of metal, the centershaft 3 is projected from at least one outer end on the axis of therotor, and the center shaft 3 is provided with a step at an outer end 4from which a small-diameter shaft 5 projects, and a separate rotor shaft6 formed with a concaved fitting hole 7 is fitted over thesmall-diameter shaft 5, thereby jointing the shafts. In this case, theother end 2 a of the rotor 1 is preferably provided with a center shaft3 a, a small-diameter shaft 5 a, a separate rotor shaft 6 a and aconcaved fitting hole 7 a which are the same as those described above.The distances from a base end 26 to the outer end 2 of the rotor whichis the rotor end face, and from a leading end 27 to the outer end 2 aresubstantially the same as the distances from a base end 26 a to theouter end 2 a of the rotor which is the rotor end face, and from aleading end 27 a to the outer end 2 a, respectively, with respect to therotor 1. FIG. 2 is a sectional view showing the screw rotor beforejointing the shafts, like numerals designate like elements and detaileddescription will be omitted.

Hereinafter, in the present invention, a rotor includes a rotor teethformed with screw teeth.

Also, as shown in FIG. 3, the shafts may be jointed by extending acenter shaft 9 from at least one outer end 8 on the axis of the rotor 1c forming the screw teeth, and the center shaft 9 is provided with aconcaved fitting hole 10 in the outer end, and by fitting a separaterotor shaft 11 projectingly provided with a small-diameter shaft 12 intothe concaved fitting hole 10. In this case, it is preferably to form aconcaved fitting hole 10 a in an outer end of the center shaft 9extending from an outer end 8 a of the rotor 1 c, a small-diameter shaft12 a is projected from the separate rotor shaft 11 a, and thesmall-diameter shaft 12 a is fitted into the concaved fitting hole 10 awhich is the same shaft-joint structure as described above. In thiscase, it is preferable that the distances between a beginning end 28 ofthe concaved fitting hole 10 formed in the center shaft of the rotor 1 cto the outer end 8 of the rotor which is the rotor end face, and betweenan innermost end 29 of the concaved fitting hole 10 and the outer end 8are substantially the same as those between the beginning end 28 a ofthe concaved fitting hole 10 a formed in the center shaft of the rotor 1c to the outer end 8 a of the rotor which is the rotor end face andbetween the innermost end 29 a of the concaved fitting hole 10 a and theouter end 8 a, respectively, with respect to the rotor 1 c.

As the shaft jointing means in each of the above described embodiments,a diameter of the hole is made smaller than a diameter of the shaft, andthe shaft is force-fitted or shrink fitted into the concaved fittinghole. Alternatively, splines are provided in the hole and the shaft tospline-connect the hole and the shaft, or the hole and the shaft arethreaded, and they may be threadedly engaged together.

Further, as shown in FIG. 4, a rotor 1 d is a rotor made ofthermosetting synthetic resin integrally molded around the center shaft13 made of metal. A center shaft 15 is projectingly provided on at leastone outer end 32 of the center shaft 13 made of metal of the rotor 1 d,a concaved fitting hole 16 is formed in the outer end of the centershaft 15, and a separate rotor shaft 17 from which a small-diametershaft 18 is projected is fitted in the concaved fitting hole 16, as ashaft joint structure of the third embodiment. This manner can bechanged into as shown in FIG. 5, a shaft joint of fourth embodiment byextending a center shaft 20 around which synthetic resin is molded fromat least one outer end 35 of the center shaft 19 made of metal of arotor 1 e, providing the outer end 21 on the center shaft 20 with a stepso that a small-diameter shaft 22 is projected therefrom, and fittingthe shaft 22 in a concaved fitting hole 24 formed in the end of a rotorshaft 23 which is separate from the rotor 1 e.

In both of the third and fourth embodiments also, it is preferable thatshaft jointing means which are the exactly the same as those shown inFIGS. 4 and 5 are provided at the outer ends 32 a and 35 a,respectively. By designating like elements with like numerals,description thereof will be omitted. Further, in this case also, it ispreferable that the distances between the beginning end 30 of theconcaved fitting hole 16 formed in the center shaft of the rotor 1 d andthe outer end 32 of the rotor and between the innermost end 31 of theconcaved fitting hole 16 and the outer end 32 are substantially the sameas those between the beginning end 30 a of the concaved fitting hole 16a formed in the center shaft of the rotor 1 d and the outer end 32 a ofthe rotor and between the innermost end 31 a of the concaved fittinghole 16 a and the outer end 32 a, respectively, with respect to therotor 1 d, and the distances between the base end 33 of thesmall-diameter shaft 22 provided on the center shaft of the rotor 1 eand the outer end 35 of the rotor and between the outermost end 34 ofthe small-diameter shaft 22 and the outer end 35 of the rotor aresubstantially the same of those between the base end 33 a of thesmall-diameter shaft 22 a provided on the center shaft of the rotor 1 eand the outer end 35 a of the rotor and between the outermost end 34 aof the small-diameter shaft 22 a and the outer end 35 a of the rotor,respectively, with respect to the rotor 1 e. Further, as shaft jointingmeans, a diameter of the hole may be made smaller than a diameter of theshaft, and preferably, the concaved fitting hole is warmed (the shaftmay be cooled) and the shaft is force-fitted in the concaved fittinghole, or splines are provided in the hole and the shaft tospline-connect the hole and the shaft, or the hole and the shaft arethreaded, and they may be threadedly engaged together. Further, atechnical means that an outer peripheral surface of the center shaft ofthe rotor around which synthetic resin of the same material as that ofthe rotor is molded may be employed.

In each of the above described first to fourth embodiments, shapes ofthe concaved fitting hole and the small-diameter shaft as shaft jointingmeans can be circular, triangular, rectangular or polygonal, andfurther, both sides of the rotor can be shaped differently such that thecenter shaft may be formed at its one end with a concaved fitting holeand projectingly provided at its other end with a small-diameter shaft.Further, as shown in FIG. 4, synthetic resin is not molded around theextended portion of the center shaft 13 made of metal of the rotor 1 d,and as shown in FIG. 5, there is a center shaft 20, the extended portionof the center shaft 19 made of metal of the rotor 1 e around whichsynthetic resin is molded. However, depending on an operating conditionor the like, synthetic resin may not be molded around the extendedportion of the center shaft 19 made of metal of the rotor 1 e, orsynthetic resin may be molded around the extended portion of the centershaft 13 made of metal of the rotor 1 d.

Further, in addition to any of the embodiments shown in FIGS. 1 to 5,the respective rotor shafts 6, 6 a, 11, 11 a, 17, 17 a, 23 and 23 a areprovided at substantially center of the axes thereof with air passageholes 25, 25 a, . . . which pass from the respective concaved fittingholes 7, 7 a, 10, 10 a, 16, 16 a, 24 and 24 a formed in the rotor shaftsor center shafts through opposite shaft end faces. Concerning theexpression of the substantially center of the axes in this case, thecenter in this case does not have to be a geometrical center of axisbecause each of the air passage holes 25, 25 a, . . . can be incommunication with the air through on any portion of each of theconcaved fitting holes 7, 7 a, 10, 10 a, 16, 16 a, 24 and 24 a;therefore, such center is called substantially center of axis in thepresent invention (a hole may be provided by penetrating a center holefor working of each rotor shaft at the time of fabrication.

Further, the material for each of the rotor shafts 6, 6 a, 23 and 23 afitted over the center shaft of the rotor is a metal material having alinear expansion coefficient smaller than that of a material used forthe center shaft. Or, the material used for the center shaft of therotor is a metal material having a linear expansion coefficient smallerthan that of the rotor shafts 11, 11 a, 17 and 17 a fitted in the centershaft.

Next, an operation and main functions will be described based on acompressor shown in FIG. 6. A rotor and separate rotor shaftsconstituted by using various shaft jointing means of each of theembodiments are not changed at all on the outside as shown in FIG. 6,and a function of the screw rotor of the screw fluid assembly is notchanged. Thereupon, functions of various technical means of the presentinvention will be described. Because the rotor and the separate shaftsare formed into separate structures, a size of rotor (including rotorteeth) can be common, and the mass production is possible using anexclusive working machine, whereas the shafts are individually workedout. And after the rotors and shafts are completed, they are fitted andjointed together by, for example, shrink fitting to form desired rotorassemblies. Therefore, the completed screw rotor assemblies are stablein working quality and performance, and it is possible to largely reducethe number of working steps and to reduce the manufacturing costs.Further, by making the parts common, it becomes easy to manage theparts.

Further, because synthetic resin is molded around the center shaft, theshaft is prevented from rusting, and even if the contact should becaused in a slight clearance of the shaft sealing portion between theoperating chamber and the bearing chamber during operation of the fluidassembly, the seizure does not take place.

Further, when the center shaft and the rotor shaft of the screw rotorare fitted, air remaining in the recess escapes outside from the airpassage hole formed in the rotor shaft. Therefore, air in the recess canflow (respiration) according to the difference in temperature during theoperation and stoppage, and joint can be maintained reliably.

Furthermore, since the linear expansion coefficient of the material atthe side fitting over the center shaft is smaller than that of the shaftto be fitted in, heat conducted due to compressing operation acts in adirection to tighten the fitting. Therefore, it is possible to reliablyhold the fitting state for a long time period. When the rotor teethportion or the rotor shaft is worn during long time operation, only arequired part should be exchanged at the time of overhaul.

FIG. 7(A) is a schematic side sectional view showing a screw rotor ofone embodiment of the present invention, and FIGS. 7 (B) to (D) areenlarged sectional views of a spiral groove or corrugated groove.

In the drawings, a shaft 41 made of metal is provided with steps 47 bypartially reducing a diameter of the shaft 41 in the axial direction,and a center shaft 38 comprising this small-diameter shaft portion isprovided at its axial peripheral surface with small spiral groove 43,thread or corrugated groove, having arc groove and crest at its crosssection. In the present embodiment, the spiral groove 43 is a singlethread, but even if it is a multiple thread, the same function andeffect can be obtained.

In FIG. 7 (B) showing an enlarged sectional view of the spiral groove43, the crest 44 where the arc profiles R of adjacent grooves 43 and 43′are connected is formed to be rounded so that the crest profile may beconnected to the profile of groove 43 by smooth curved profile in orderto make the peripheral surface of the shaft 38 no angle portion.

As shown in FIG. 7 (B), in the cross section of the spiral groove 43, aradius r of the rounded crest 44 is made different from a radius R ofthe arc groove, for example, a semi radius axis, but as shown in FIG. 7(c), a radius of said r may be set to a length R which is the same asthe arc groove, and the arcs can directly be connected.

Further, the shape of the cross section may be a ridge shape connectingthe arcs r forming the groove and crest by straight line, orsubstantially Whit worth thread shape (see FIG. 7 (D)).

Referring again to FIG. 7 (A), the spiral groove 43 is a spiral groovehaving an opposite revolutional direction with respect to a revolutionaldirection when the screw rotor is operating. That is, when a male rotoris rotated right-handed or clockwise direction as viewing from theintake side shaft end, the spiral groove 43 is previously structured forleft-hand revolution, and a female rotor shaft meshed with the malerotor is formed with spiral groove of right-hand revolution.

The center shaft 38 comprising a small-diameter shaft portion having thespiral groove 43 is provided at its both ends with small-diameter shaftportion slightly smaller than the spiral groove 43 to provide millingundercut (grooves) for cutting blade for working out the spiral groove43.

If a shaft diameter D2 of the center shaft 38 comprising thesmall-diameter shaft portion having the spiral groove 43 is set smallerthan a shaft diameter D1 of the rotor shaft 36 (D1>D2), it is possibleto increase a distance h between a peripheral surface of the centershatf 38 around which the synthetic resin is molded and a bottom of thetooth groove (shown by dotted line) of the synthetic resin rotor.Therefore, even if a crack is generaited in the synthetic resin in thevicinity of the shaft portion, it is very rare that the crack reachesthe teeth space of the rotor.

A depth of the groove of the spiral groove 43 is relatively shallowcompared with the diameter of the shaft. For example, the depth and thediameter are in the ratio of about 1%. This arrangement reduces thethermal shrink stress generated around the portion of the syntheticresin molded around the groove to a small degree.

46 denotes a tooth of synthetic resin rotor 1 f molded around the shaft41.

47 denotes a step provide on the shaft 41 for supporting an axial thrustof the rotor 1 f. The angle portion of the step 47 is rounded at smallscale arc R or chamfered so as to avoid stress concentration.

In the present embodiment, when glass phenol resin having phenol resinand glass fiber as main component is used for example as the syntheticresin to be molded around the shaft 41, since the linear expansioncoefficient of the synthetic resin is similar to that of metal (here,steel or cast iron), in a compressor using such a rotor, it is possibleto reduces the stress generated due to a difference in thermal shrinkingamount between the shaft 41 and the rotor 1 f during the operation andstoppage to a small degree.

The synthetic resin for the rotor is not limited to the glass phenolresin; any component of a resin can be used for the rotor if the resinsatisfies the characteristics such as mechanical strength and canminimize at the smallest possible stress generated due to thermal changeby using such synthetic resin having the thermal expansion coefficientsimilar to the linear expansion coefficient of the shaft material.

FIG. 8 shows a partial sectional view of a screw rotor of anotherembodiment of the present invention. Among the numerals indicated in thedrawing, the elements having the same numerals as those in FIG. 7 (A)show the common elements of said embodiment.

In the present embodiment in which a shaft diameter D4 of a portion ofthe shaft 41 around which synthetic resin is molded and which has thespiral groove 43 is greater than a shaft diameter D3 of the shaft 41including intake side and discharge side of the rotor shaft 36 (D4>D3),surface area of a portion provided with the spiral (corrugated) groove43 is increased, which reinforces the fixing force between the shaft 41and the rotor 1 f.

At that time, since it is unnecessary to provide the groove 41 with amilling undercut groove for working out the spiral groove 43, there isno possibility to lower the strength of the shaft 41. The step 47provided between the shaft diameter D4 and the shaft diameter D3supports the thrust force acting on the rotor 1 f made of syntheticresin. The shape of the step 47 is as described above.

In the present embodiment, when a distance between an outer peripheralsurface of the center shaft 38 on which the spiral groove 43 is formedand an outer periphery of the rotor 1 f is denoted by A2, and a distancebetween the end face of the rotor 1 f and the step 47 of the shaft 41 onwhich the spiral groove 43 is formed is denoted by A1, if A1=A2, acooling speed of the synthetic resin material in the vicinity of theshaft 41 is uniformed during the cooling of the synthetic resin rotor 1f after it is molded, and internal stress generated in the rotor isreduced and therefore, the possibility of crack generated in thesynthetic resin is reduced.

In the case of the present embodiment also, a shape of a cross sectionof the spiral groove 43 can be the groove shape as shown in FIG. 7.

FIG. 9 shows a partial sectional view of a water-injection type screwcompressor of a screw rotor of another embodiment of the presentinvention. A step is provided between the intake side shaft sealingportion and discharge side shaft sealing portion so that the diameter ofthe center shaft 38 may be smaller than that of the shaft 41 includingthe intake side and discharge side rotor shafts 36, and the center shaft38 comprising the small-diameter shaft portion is provided at its axialperipheral surface with a spiral groove or corrugated groove.

Preferably, the steps are provided in such a way that L (the distancebetween two steps) may be longer than a distance between the intake sideand discharge side water-shaft sealing devices, and may be shorter thana distance between the intake side and discharge side oil-shaft sealingdevices. The shafts 48 around which synthetic resin is molded and inwhich shaft sealing devices are fitted are integrally and continuouslyextending at both opposite end faces of the rotor 1 f.

The numerals are denoted in common to the description of FIG. 7.

In the case of the present embodiment, since a range L in which thesteps are provided can be long, the axial length of portion on which thespiral groove or corrugated groove is formed is long, and the surfacearea of the shaft is increased and the fixing strength between the shaft41 and the synthetic resin rotor is increased. Further, synthetic resinis molded around the shaft in which the water-shaft sealing device isfitted and therefore, even if it is used for the water-injection typescrew compressor, rust is not generated on the rotor, the shaft and thelike.

FIG. 10 is a partial sectional view of a screw rotor of anotherembodiment of the present invention, and the numerals are used in commonto those in the descriptions of FIGS. 7 to 9.

In the case of the present embodiment, the diameter of the shaft portion(a portion on which the spiral groove 43, is formed) around whichsynthetic resin is molded, forming the shaft sealing portion, is smallerthan the diameter of the shaft portion (a portion on which the spiralgroove 43 is formed) around which synthetic resin forming the rotor 1 fis molded, thereby providing a plurality of steps 47 therebetween tosecure a thickness of the synthetic resin forming the shaft sealingportion to prevent crack from being generated in the synthetic resin.

Further, the depth of groove of the spiral groove 43, is made shallowerthan the depth of groove of the spiral groove 43, thereby preventingcrack from being generated in the synthetic resin which forms the shaftsealing portion.

The above described groove is not limited to a spiral groove, and if acorrugated groove is formed, the same effect can be obtained.

In the present embodiment, since the diameter of the shaft portionaround which synthetic resin is molded (a portion on which the spiralgroove 43 is formed) is relatively large, and the axial length of theportion on which the spiral groove is formed is long, the surface areaof the shaft is increased so that the fixing strength between the shaft41 and the synthetic resin rotor 1 f can be increased.

FIG. 11 is a partial sectional view of another embodiment, and thenumerals are used in common to those in the descriptions of FIGS. 7 to10.

The present embodiment can be called as a modification of the rotorshaft shown in FIG. 10. In the rotor the shaft portion around whichsynthetic resin is molded is formed by smooth curved lines, and a shaft41 including center shaft 38 as a whole is provided at its axiallycentral portion with an expanded portion.

Corrugated grooves or spiral grooves 43 are formed on the entireperipheral surface of the shaft portion around which synthetic resin ismolded.

According to the present embodiment, arc surfaces of the center shaft 38disperse and support the thrust acting on the rotor 1 f. Therefore,stress is not concentrated, and the possibility of cracks of syntheticresin is reduced.

Although it is not illustrated in the drawings, if the shaft 41 iscasted, and the shaft 41 around which synthetic resin is molded is leftas casted state (cast sands attached on the surface are completedremoved), and if the shaft surface except the portions around whichsynthetic resin is molded is finished by mechanical working, syntheticresin enters into uneven surface of the casted surface of the shaftaround which synthetic resin is molded, and the fixing structure betweenthe shaft and the rotor can be strengthened, and the number of workingsteps can be reduced.

The present invention is so constituted as explained above, and has theeffects described below.

Firstly and secondly, since the rotor and the shaft of the screw rotorare of separate structures, if the size of the rotor is the same, thesame working process can be used for the rotor, thereby the productivityis improved, and stable working quality can be maintained, and it iseasy to manage the parts. Further, by employing a simple shaftconnection, the same rotor can be employed for various assemblies havingdifferent shaft lengths, which eliminates waste of screw rotor materialsand unnecessitates the large number of working steps to reduce thecosts, and the shafts can be divided and handling thereof is easy, thelength of the shaft can be shortened so that a molding machine can bereduced in size, working of a shaft for exclusive use among the variousmachines suffices, working of the shaft is easy, and the manufacturingcosts can largely be lowered. Further, as to the shaft, even in aprocess consisting of surface treatment and other complicatedfabrication steps, the parts themselves are smaller than the rotor,handling thereof is easy and working efficiency is excellent.

Thirdly, in addition to any of the first and second effects, it ispossible to prevent assembling error between the rotor and the rotorshaft, the working parts are made common, and further reduction ofmanufacturing costs can be achieved.

Fourthly and fifthly, in addition to any of the first to third effects,since synthetic resin is molded around the center shaft, only necessaryportions can be easily subjected to the rust preventing treatment orsurface treatment, and anticorrosive material can easily be employed.

Sixthly, in addition to any of the first to fifth effects, by forming anair passage hole penetrating from the concaved fitting hole formed inthe rotor shaft or center shaft to the shaft end opposite to the saidhole, the shaft connection is smoothly fitted, and such an insertionoperation is easily and reliably conducted, and air in the recess canflow (respiration) according to the difference in temperature of therecess during the operation and during the stoppage.

Seventhly and eighthly, in addition to any of the first to sixtheffects, since a linear expansion coefficient of a material of the shaftthe side of which is fitted over the center shaft is smaller than thatof the center shaft, a force acts in a direction to fasten the fittingcondition by conduction heat according to compressing effect to reliablyhold the fitted state for a long time of period.

Further, ninthly, a spiral groove or corrugated groove connecting thecrest and groove profiles by smooth curved line are formed on the shaftperipheral surface around which synthetic resin is molded. Therefore,stress concentration on the fixing portion at the side of the rotor ismoderated, and crack generated from the fixing surface toward the toothbottom of the screw rotor groove can be prevented, and the shaft and therotor (synthetic resin portion) can be prevented from separating, andthe fixing state therebetween can be strengthened and maintained for along time period.

Tenthly, by providing the shaft with a step or expanded portion, theaxial movement of the rotor is restrained, and even if the shaft and therotor are separated by any reasons, damaging accident such as contactbetween the inner surface of the casing and the rotor end face orseizure during operation of the compressor is prevented.

Eleventhly, when the present invention is employed in thewater-injection type screw compressor, no rust is generated on a portionwhich contacts with water, which enhance the reliability of the sealingdevice, and rust or oil is not mixed into discharged air. Further, sinceit is possible to prevent the deterioration or emulsification of thelubricant oil due to mixture of the water into the lubricant oil, thelife span of the bearing can be elongated.

Twelfthly, even if the shaft is made of steel or cast iron, it isunnecessary to subject the shaft surface to plating or coating for rustprevention, and the working time can be shortened as compared with theconventional device, and the screw rotor can be manufactured at lowercosts.

Thirteenthly, the present invention is not limited for use for the rotorof the water-injection type screw compressor, but it can be used forrotors for screw fluid assembly such as oil-cooling type screwcompressor, oil free screw compressor, screw vacuum pump or screwexpander.

Thus, the broadest claims that follow are not directed to a machine thatis configured in a specific way. Instead, said broadest claims areintended to protect the heart or essence of this breakthrough invention.This invention is clearly new and useful. Moreover, it was not obviousto those of ordinary skill in the art at the time it was made, in viewof the prior art when considered as a whole.

Moreover, in view of the revolutionary nature of this invention, it isclearly a pioneering invention. As such, the claims that follow areentitled to very broad interpretation so as to protect the heart of thisinvention, as a matter of law.

It will thus be seen that the objects set forth above, and those madeapparent from the foregoing description, are efficiently attained andsince certain changes may be made in the above construction withoutdeparting from the scope of the invention, it is intended that allmatters contained in the foregoing description or shown in theaccompanying drawings shall be interrupted as illustrative and not in alimiting sense. It is also to be understood that the following claimsare intended to cover all of the generic and specific features of theinvention herein described, and all statements of the scope of theinvention which, as a matter of language, might be said to falltherebetween.

Now that the invention has been described;

For your reference

[Drawing to be selected for an abstract] FIG. 1

[Explanation of Numerals]

1, 1 b, 1 c rotor

1 d, 1 e, 1 f synthetic resin rotor

2, 2 a, 8, 8 a, 32, 32 a, 35, 35 a outer end of rotor

3, 3 a, 9, 9 a, 15, 15 a, 20, 20 a center shaft

4, 4 a, 21, 21 a outer end of center shaft

5, 5 a, 12, 12 a, 18, 18 a, 22, 22 a smaller-diameter portion

6, 6 a, 11, 11 a, 17, 17 a, 23, 23 a, 36 rotor shaft

7, 7 a, 10, 10 a, 16, 16 a, 24, 24 a concaved fitting hole

13, 19 center shaft made of metal

25, 25 a air passage hole

38 smaller-diameter shaft portion (center shaft comprising the saidportion)

41 the entire shaft (comprising center shaft and rotor shaft)

43, 431 spiral groove

44 crest (shaped) portion

46 tooth (groove)

47 step

48 shaft (sealing) portion around which synthetic resin is molded

39 groove having square cross section

51 crack

What is claimed is:
 1. A shaft structure of a screv rotor for a screwfluid assembly, wherein a shaft made of metal around which syntheticresin is molded is provided at, at least, its center shaft with a step,a surface of said shaft around which said synthetic resin is molded isprovided with a spiral groove or corrugated groove, in a cross sectionof said spiral groove or corrugated groove taken along the planeincluding the center line of said shaft, the arc profile of adjacentspiral or corrugated grooves are connected by smooth curved and roundedline, and said spiral groove is formed in the opposite revolutionaldirection with respect to a revolutional direction of said screw rotor,and a rotor made of synthetic resin is molded around said shaft made ofmetal.
 2. A shaft structure of a screw rotor for a screw fluid assembly,wherein a shaft made of metal around which synthetic resin is molded isprovided with a step and/or expanded portion, and a surface of saidshaft around which synthetic resin is molded is provided with acorrugated groove or spiral groove, and in a cross section of saidspiral groove or corrugated groove taken along the plane including thecenter line of said shaft, the arc profile of adjacent spiral orcorrugated grooves are connected by smooth curved and rounded line. 3.The shaft structure of a screw rotor according to claims 1 or 2, whereinsynthetic resin is molded around said surface of said shaft continuouslywith said rotor made of synthetic resin, and synthetic resin is moldedon an axial peripheral surface of a portion of said shaft at leastbetween a shaft sealing portion at an intake side and a shaft sealingportion at a discharge side.
 4. The shaft structure of a screw rotoraccording to claims 1 or 2, wherein synthetic resin which is the same asthat of said rotor is molded around a surface of outer periphery ofcenter shaft of said rotor.
 5. The shaft structure of a screw rotoraccording to claim 4, wherein said rotor shaft is formed substantiallyat its center of axis with an air passage hole passing from a concavedfitting hole formed in said rotor shaft or center shaft through theopposite shaft end.
 6. The shaft structure of a screw rotor according toclaim 5, wherein a material of said rotor shaft which is fitted oversaid center shaft of said rotor has a linear expansion coefficientsmaller than that of a material used for said center shaft.
 7. The shaftstructure of a screw rotor according to claim 5, wherein a material usedfor said center shaft of said rotor has a linear expansion coefficientsmaller than that of said rotor shaft which is fitted into said centershaft.